Hydraulic motor with rotating radial cylinder block and reciprocating pistons reacting against outside annular grooved cam



Dec. 21", 1948. R. F. HORTON HYDRAULIC MOTOR WITH ROTATING RADIAL CYLINDER BLOCK AND RECIPROCATING PISTONS REACTING AGAINST OUTSIDE ANNULAR GROOVED CAM 4 Sheets-Sheet 1 Filed Nov. 11, 1944 ATTORNEY BYWW 'Z HIIIIIIII I ll N N N mm .m. H

R. F. HORTON HYDRAULIC MOTOR WITH ROTATING RADIAL CYLINDER Dec. 21, 1948. #157,100

BLOCK AND RECIPROCATING PISTONS REACTING AGAINST OUTSIDE ANNULAR GROOVED CAM 4 Sheets-Sheet 2 Filed Nov. 11, 1944 5 i FF Q AT Q l MN I -I||&H. w M R. (m 1.0 1-1 a Q .W L :m q Nb wm M] h m ww INN m M 1 PM n Q A @o mm a m w L \V N% \N ww w Q Q .Q

INVENTOR E/P fi flO/POM WM? ATTORNEY Dec. 21, 1948. R. F. HORTON HYDRAULIC MOTOR WITH ROTATING RADIAL CYLINDER- BLOCK AND RECIPROCATING PISTONS REACTING AGAINST OUTSIDE ANNULAR GROOVED CAM 4 Sheets-Sheet 3 Fil'i Nov. 11, 1944 BY I AI'TCRNEY HUM. .H I .FT .H L L Dec. 21, 1948. R. F. HORTON 2,457,100- HYDRAULIC MOTOR WITH ROTATING RADIAL CYLINDER I BLOCK AND RECIPROCATING PISTONS REACTING' AGAINST OUTSIDE ANNULAR GROOVED CAM 4 Sheets-Sheet 4 Filed Nov. 11, 1944 a w w R O T N E v fear A rf airolv.

ATTORNE Patented Dec. 21, 1948- umrso STATES PATEN OFFICE HYDRAULIC MOTOR WITH ROTATING RA- DIAL CYLINDER BLOCK AND RECIPRO- CATING PISTONS REACTING AGAINST OUTSIDE ANNULAR GROOVE!) CAM Roger F. Horton, Hempstead, N. Y. Application November 11, 1944, Serial No. 562,947

24 Claims. 1

This invention relates to an hydraulic motor.

An object of the invention is to provide a simple, economical, and efficient hydraulic motor adapted for operation at high pressures.

Another object of the invention is to provide an hydraulic motor having ,less internal friction and therefore less power loss within the motor than has heretofore been attainable.

Another object of the invention is to provide a high speed hydraulic motor having, a greater horsepower output per pound of weight than has heretofore been available.

Another object of the invention is to provide means for increasing the centrifugal energy of used or spent propulsion fluid revolving within the motor casing.

Another object of the invention is to utilize heretofore unused means without further complicating the mechanism'for the expulsion under pressure of the used propulsion fluid.

Another object of the invention is to provide an hydraulic motor in which the direction of flow of the propulsion fluid may be reversed caus= ing reverse rotation of the mechanical output shaft without the necessity of a third conduit usually required to conduct internal leakage back to the propulsion fluid reservoir.

Another object is to provide an hydraulic motor which may be driven, instead of itself driving, by an outside mechanical source, without cavitation or other effect injurious to the working mechanism.

Another object is to provide an hydraulic mo tor in which sliding friction is almost entirely replaced by rolling friction, thereby permitting higher speeds and higher loading per square inch of bearing surface.

Another object is to provide an hydraulic motor with integralmeans for increasing the pressure differential between the incoming high pressure fluid and the outgoing spent fluid.

Other objects of the invention will be in part obvious or in part pointed out hereinafter.

The invention accordingly consists in the features of construction, combinations of elements,

arrangements of parts, and in the several steps and relation and order of each of said steps to one or more of the others thereof, all as will be pointed out in the following description, and the scope of the application of which will be indicated in the following claims.

The invention will best be understood if the following description is read in connection with the drawings, in which,

Figure l is a schematic view of a system for converting mechanical power into hydraulic energy and back to mechanical energy, including an hydraulic motor; I

Figure 2 is a. view of the hydraulic motor and four-way valve shown in Figure 1, with the valve in cross-over position and indicating opposite rotation of the output shaft of the motor;

Figure 3 is a front elevation partly cut away and partly in vertical section taken on the line 33 of Figure 4;

Figure 4 is a side elevation taken on median line 4-4 of Figure 3 in a. vertical plane passing through the axis of the motor, partly cut away and partly in section;

Figure 5 is a side view of the p'intle indicated in Figure 4, showing the sliding valve sleeves and connecting fluid ports and conduits, in their rev spective position for the setting of the cross-over valve as shown in Figure 2;

Figure 6 is a vertical transverse section taken on line 6--t of Figure 5;

Figure '7 is a front elevation showing the discharge path of the propulsion fluid;

Figure 8 is a transverse section taken on the line 88 01 Figure 7;

Figure 9 is a view similar to Figure 5 but showing the sliding valve sleeves in their posi t cn for the propulsion fluid flow as indicatedin Figure 1;

Figure 9 is a view similar to Figure 9 but showing the valve members in opposite phase from their positions in Figure 9 for a flow of propulsion fluid in the direction opposite to that illustrated in Figure 9;

Figure 10 is a detail view .of one of the track ring supporting members shown in Figure 4;

Figure 10* is a side view of a section of the member shown in Figure 10;

Figure 11 is a detail view in vertical section showing the unbalanced nature of the frictional contact between the respective pistons of the radial cylinder block and a grooved surface of the track ring;

Figure 12 is a plan view partly in section on the line l2-l2, of the detail shown in Figure 11;

Figure 13 is a detail side view of one of the sliding sleeve valves of the pintle showing valve means for the sleeve port adjacent its anti-drive end; and

Figure 14 is a vertical cross sectional view taken on the line l4l4 of Figure 13.

In the following description the term drive end" is used with respect to elements of the motor to indicate the end which is nearer or extending toward the mechanical output side of the motor, and the term "anti-drive end" is used to indicate the end extending toward, or which is nearer the hydraulic input side of the motor.

In Figure 1 I have shown a fluid circuit including a fluid reservoir l0, hydraulic pump II.

a speed control valve II, a four-way direction control valve l3, and an hydraulic motor, indi2ated generally by the numeral ll, interconnected by suitable conduits to form a closed circuit adapted to convert mechanical power, applied at spline ii of pump ll, into hydraulic power, and to reconvert it, by means of motor ll through spline l8, again into mechanical power.

The four-way valve I3 is of any well known type and is not described in detail herein as it per se forms no part oi my invention. It will be readily understood by those skilled in the art that by the operation of valve arm Ila, from the position shown in full lines in Figure 1 to its position shown in full lines in Figure 2, the direction of flow through the portion of the circuit on the drive side of valve it will be reversed whereas the direction of. flow through the remainder, or anti-drive side of the circuit will remain the same. As will be more fully described herein the motor I l is so devised that when valve I3 is shifted a pressure change is created within motor I serving to automatically operate valve means controlling the direction of rotation of the motor rotor and thus reversing the drive of the motor.

Motor i5 comprises a closure consisting of a combined casing I1 and mounting flange l8, and a casing cover l9, the cover it being joined to the casing I? as by machine screws lSa. The casing cover I9 is provided with a central bore into which extends the pintle to having the flange 20a overlying the outer face of casing cover 59 and being secured thereto by the studs 2! and nuts 22, respectively. Pintle 20 has at its drive end a wearing plug 23 which abuts against wearing plug 24 fixed in the anti-drive end of the hollow drive shaft 25 which carries at its other extremity the aforesaid spline IS.

The pintle 20 is provided with two longitudinally extending bores 28 and 2?, respectively, in which are inserted the sliding sleeve valves 28 and 29, respectively, closed at the drive end but open at the anti-drive end. The bores 26 and 21 respectively, adjacent the drive end of pintle 2d, are internally threaded to receive the externally threaded stop and spring retaining member to,

and, between the said stop and the drive ends of the sliding sleeves 28 and 2d, respectively, compression springs 38 are provided, said springs tending to position the said sliding sleeves near the anti-drive endgof the bores, respectively in the position of sleeve 28 as illustrated in Figure 5, except when said sleeves are in communication with the high pressure side of the system in which case the particular sliding sleeve so connected with the high pressure line is moved to the position of sliding sleeve 29 in Figure 5 against the bias of its spring 35. It is immediately returned to its initial position when it is disconnected from the high pressure side of the system.

The two hollow sliding sleeves 28 and 29 are each provided with two laterally opening ports, 32 and 33, and 3t and 85, respectively. The port 32 of sleeve 28 is adapted to register with port 36 0f the pintle shell when the bore 26 is connected with the high pressure side of the system and the sleeve is held at the drive end of bore 28 by the pressure of the propulsion fluid acting against 4 its spring ll. The port 83 of sleeve 20 is adapted to register with port 31 of the pintle shell when the bore 28 is connected with the low pressure side of the system, sleeve 28 being then positioned by its spring 3| at the anti-drive end of bore 28. Similarly port 34 of sliding sleeve 28 is adapted to register with port 88 of the pintle shell when the bore 21 is connected with the high pressure side of the system and the sleeve 29 is held at the drive end of bore 21 by the pressure of the propulsion fluid acting against the spring loading of the valve sleeve, and port 85 of sleeve 28 is adapted to register with port 31 of the pintle shell when the bore 21 is connected to the low pressure or return side of thesystem, and the valve, due to its spring loading, is positioned at the antidrive end of its bore. Port 38 is circumferentially spaced from port 36, in the pintle shell, and port 31, which communicates with both bores 28 and 21, is spaced longitudinally of the pintle from the ports 36 and 38, toward the anti-drive end of the pintle.

Revolvably mounted on pintle 2B is a rotor assembly 39 comprising the radial cylinder block 38 having cylinders 39a, preferably seven in number, in the bores of which pistons, 40, are freely mounted, so that they are slideable towards and away from the axis of the pintle 20 and also rotatable about their respective longitudinal axes, said pistons 40 are each provided with a head in the form of a spherical segment 4!, having a top or relief area 52. The piston heads are each adapted to contact a groove 53, provided in the inner surface of track ring 8%, in which said pistonstt travel and by reason of the top or relief area d2, contact between the piston heads ti and the track ring groove ts is confined to the spherical surface of the spherically segmented heads ti. The radius of the surface of each of the spherical segments dl of the pistons and that of the track ring groove d3 are substantially the same and a condition of congruity exists between the surfaces generated by the two radii except for inconsistent surface irreguiarities which are within even close tolerance limits and predominate in the track ring groove 83 due to the inherent limitations in machining, shaping, and finishing operations employed. Because of these surface irregularities there will be in practice a condition of unbalance of the frictional forces on diametrically opposite sides of the piston heads ti which will cause the pistons so to rotate in an oscillatory manner, and in either direction of rotation, as the pistons travel around the groove 63. Accordingly there will be a frictional force F on one side of the longitudinal axis of the piston dd, greater thanthe theoretically balanced forces, (Figure 12) and pistons 80 rotate in an oscillatory manner within their respective cylinders about their own longitudinal axes respectively, as well as about the axis of rotation oi the pintle with the rotor during their reciprocal action, as shown in Figures 11 and 12.

Track ring 46 is supported by the ring support! ing cup-shaped members 45 and 56, arranged in opposed, laterally spaced relation, and the bearings d? and 68 respectively, positioned concentrically around the outwardly extending flange portions of the ring retaining members $5 and as respectively, which are seated respectively in eccentric bores provided therefor in diametrically opposed relation in the inner faces of casing I1, and casing cover it, respectively.

At the drive end of radial cylinder block 39 an annular fla ge is provided and a circle of spaced aesmoo holes extending parallel with the cylinder bloclr axis are formed therein, and the internal ace of flange as is then ground out to convert the holes, throughout a portion of their depth, into the half holes or semi-cylindrical bores 63. A similar circle of holes is provided in the anti-drive end of radial flange 5| of drive shaft 25, and flange 5i is ground externally to similarly convert the said holes, throughout a portion of their length, into the half holes or semi-cylindrical bores Ela, the diameter of radial flange iii of the drive shaft being related to the diameter of the said annular flange of the cylinder block so that the half holes of flange 5i may complement the half holes of flange 39 to form complete cylindrical spaces,.

- packing 32 may be provided between collar 3i and shaft 25, and also suitable packing may be provided between the collar 6! and end plate 63 secured to mounting flange i8 as by screws 63a. Preferably packing 62 is of an oil resisting material such as neoprene. The packing between collar SI and end plate 63 may desirably comprise a ring 64 of morganite or bronze having a lapped surface pressed against the lapped surface of a ring 65 of cast iron by action of collar 3i. Preferably also an oil seal 68 is provided between the mounting flange i3 and the end plate Assuming that the flow direction control valve i3 is set as indicated in Figure 2, propulsion fluid from reservoir in, after being energized by pump it, and after passing through speed control valve IE, will enter pintle 29 through conduit 52, which communicates with the open end of sliding sleeve 29, through the anti-drive end of bore 2?. Due to the pressure of the incoming fluid, sleeve as will be moved to the position shown in Figure 5, with its port out of registry with port 3? through the pintle shell, but with its port 33 in communication with port 38 through the pintle shell, which communicates, through the interior of radial cylinder block 39, with the inner ends of the bores of the cylinders 3911 respectively. The incoming flow of fluid under pressure will thus force pistons outwardly in the bores of cylinders 39a respectively against ring t3, and the angle between the axes of the pistons and the surface of the ring will cause the radial cylinder block 39 to rotate. At the same time the frictional contact between the spherical heads of the pistons Ml and ring 43 will cause ring 4% to be revolved at substantially the same rate asthe radial cylinder block, thus largely eliminating all sliding friction between the pistons 43 and the ring 46.

As the pistons again move inwardly in the bores of cylinders 39a, due to the eccentricity of the track ring, the propulsion fluid is now successively returned from the piston bores into the pintle through port 36, and then flows into the space within the motor housing through the drive and of pintle bore 26, at substantially the center of the motor housing. The ring support members t5 and 58 are provided with outwardly opening radially extending slots 53 provided in their radially extending wall portions respectively. Propulsion fluid entering the interior portion of the motor casing through the open end of pintle bore 26 flows in and fllls the space surrounding the cylinder block 39, and fills the radial slots 53, and is discharged from said slots by centrifugal force engendered by the rotation of the cylinder block and track ring assembly. The fluid thus forcibly discharged from slots 53 adds to the centrifugal force of the fluid in the casing which is thus discharged with added force into the outlet port 5 3, where it is diverted into the laterally projecting discharge conduit which leads through the wall of casing cover i9 back to port 56, which is in register with port 37 of the pintle shell, which in turn communicates with either the sliding sleeve 28 through port 33, or sliding sleeve member 29 through port 35, depending on which of said sliding sleeves is in communication with the low pressure or return side of the fluid system. Under the conditions assumed the drive shaft 25 and spline i6 will rotate in a counterclockwise direction and the return flow will be through conduit 55 and port 56, Figure 8, through pintle shell port 31, into sliding sleeve 28 through port 33, and back through conduit 520, through four-way valve i3 which is positioned for crossover as illustrated in Figure 2, and back to reservoir l0. If, on the other hand, cross-over valve-l3 is in the position illustrated in Figure l the fluid flow will be from reservoir i0 throught pump ll, through speed control valve i2, through flow direction valve l3, through conduit 520. into the interior of sliding sleeve 28, which will be positioned as illustrated in Figure 9, through sliding sleeve valve 32 and port 33 of the pintle shell into the rotor hub and into the lower end of the bores of the cylinder 3M, and into contact with pistons 40 from which it will be returned through pintle shell port 38, port 3d of sliding sleeve 29 and then outwardly through the open drive end of pintle bore 2?, into the interior of the motor housing casing from which it will be returned by the centrifugal action afforded by slots 53 discharging into port 5% return conduct 55 terminating in port 56 which registers with port 371 in the pintle shell with which port 35 of sliding sleeve 29 will now be in register and thus through the anti-drive end of sliding sleeve 29 into con duit 35 directly back to reservoir id. With this flow motor output shaft 25 and spline it will rotate in a clockwise direction.

To prevent propulsion fluid from short circuiting from ports 33 to port 35 through pintle shell port 3?, or for the reverse operation of the motor to prevent fluid from. short circuiting from port 35 to port 33 through pintle shell port 37 when the motor is initially started at which time both sliding sleeves 28 and 29 will be at the anti-drive end of their respective bores, I preferably provide in the interior of each sliding sleeve a neoprene sleeve-check-valve 58 extending across ports 33 and 35 respectively and retained in position by means of the steel spring support member 59 which is open at both ends and is attached to sleeve 58 in any suitable way as by a moving engagement with the neoprene sleeve 53. The escape of fluid outwardly through either port 33 or 35, as the case may be, will be prevented by neoprene sleeve 58 since the high pressure fluid will tend to expand the sleeve outwardly thus flrmly sealing port 33 or 35 of the slidable sleeve through which the high pressure v 7 4 fluid is flowing into the motor, it will also be understood that sleeve 58 will not prevent the return flow of the fluid from return conduit 55 through port 56 and pintle shell port 31 since the weight and pressure of the liquid will press and distort the neoprene check valve 58 thus allowing the return fluid to enter port 33 or 35, according to which of the sliding sleeves is in communication with the low pressure side of the system, to return the fluid to the reservoir.-

Radial slots 53 are provided in support members 45 and 46, asstated above, to add centrifugal energy to the propulsion fluid in the casing in order to forcibly expel it from the motor after it has performed its propulsive work. Since the propulsion fluid within the casing, and particularly the portion which is radially beyond the track ring 44, is rotating with the track ring and the ring supporting members 45 and N, prior to discharge, the force of discharge or centrifugal force can be calculated from the formula F=M?w where M mass of fluid under consideration;

the distance from the mass center of the fluid to the center of rotation; and m the angular velocity of this mass center. about the center of rotation.

In order to increase the pressure differential between the low and high pressure sides of the motor, to thereby attain an increased rate of flow of the .propulsion fluid and correspondingly increased motor speed I find it is desirable to increase all elements in the above equation by proper arrangement of radial slots 52, the eccentric center of track ring 44, and the discharge port 54. It will be seen by reference to Figures 3 and 8 that this is accomplished as follows: center of the discharge port 54 and the eccentric center, a, of the track ring, are located on diametrically opposite sides of the center, b, of the pintle. This arrangement provides in eifect two semi-circular complementary chambers c and c, which together completely encircle the track,ring 44, and which are identical in size and shape, each having a constantly increasing mean radius. Only one of these chambers is active in adding centrifugal force to the propulsion fluid for each direction of rotation of the rotor assembly. The constantly increasing mean radius of the chamber which is active, and into which fluid is continuously being forced'by the radial slots 53, provides a constantly increasing M, or mass, as the fluid approaches the discharge port 54, and also provides a constantly increasing corresponding increase in the angular velocity of the fluid approaching the discharge port 54. Thus, since all three elements of the equation are constantly increasing there is provided a simple and efiective centrifugal pump serving to forcibly expel spent propulsion fluid, thereby reducing back pressure on the working cylinders,

and making it possible net work.

The hydraulic motor described herein has the advantage that it will rotate freely, and without cavitation when the flow of propulsion fluid is cut on and the motor continues to rotate for any reason, such for example as the momentum of its load. When the supply of fluid is cut off the sliding sleeve valves are both moved to the antidrive and of their respectlve bores and the motor stays full of propulsion fluid, and as the motor continues to rotate fluid is simply pumped from the discharge side of the cylinder block to the intake side of the cylinder block through the drive end of the bores of the pintle. As a result my motor can be driven'mechanically for short periods, without injury or pounding.

Itwill thus be seen that there has been provided by this invention an apparatus in which the various objects hereinabove set forth tofor them to perform more gether with many thoroughly practical advantages are successfully achieved. As various possible embodiments might be made of the mechanical features of the above invention and as the art herein described might be varied in various parts, all without departing from the scope of the invention, it is to be understood that all mat ter hereinbefore set forth or shown in the ac-,

companying' drawings is to be interpreted as illustrative and not in a limiting sense.

What I claim is 1. In a radial motor, a casing, a pintle mounted centrally in: the casing and having a port to re- The 40 ceive low pressure propulsion fluid for discharge from said motor, a discharge conduit extending through the casing wall and communicating between the interior of the casing and said port, and a rotor assembly rotatable in said casing around said pintle including a radial cylinder block, a track ring, and radially extending support means therefor'having outwardly opening radial slots adapted, when said assembly is rotating, to incmase the centrifugal force of propulsion fluid in said casing, said pintle having a plurality of bores communicating with the interior of the casing and a plurality of circumferentially spaced ports communicating between. said bores respectively and the interior of said cylinder block, and pressure responsive valve means in said bores adapted to connect the cylinder block with which ever bore is supplied with high pressure propulsion fluid, and to connect the cylinder block with the space in the casing around said cylinder block through the other of said bores.

2. In a radial motor, a casing, a pintle mounted centrally in the casing and having a port to receive low pressure propulsion fluid for discharge from said motor, a discharge conduit extending through the casing wall and communicating between the interior of the casing and said port, and a rotor'assemhly rotatable in said casing around said pintle including a radial cylinder block, a track ring, and radially extending support means therefor having outwardly opening radial slots adapted, when said assembly is rotating, to increase the centrifugal force of propulsion fluid in said casing, said pintle having a plurality of bores commimicating with the interior of the casing and a plurality of circumferentially spaced ports communicating between said bores respectively and the interior of said cylinder block, and pressure responsive valve means in said bores adapted to connect the eviinc 1r block with whichever bore is supplied with high pressure propulsion fluid. and to connect the cylinder block with the spacezin the casing around said cylinder block through theother of said bores and simultaneously to connect said other bore and the said pintle port which communicates with said discharge conduit.

3. In a radial power converter, a rotatable cylinder block having a number of radial cylinders and pistons in said cylinders respectively, and a rotatable track ring engaged by said pistons, the heads of said pistons being spherical the casing wall and communicating between the interior of the casing and said port.

5. In a radial motor, a casing, a pintle mounted centrally in the casing and having a port to receive low pressure propulsion fluid for discharge from the motor, a conduit extending through the casing wall and communicating between the interior of the casing and said port, and an assembly rotatable in said casing around said pintle including radial members having outwardly opening radial slots adapted when said assembly is rotating to add centrifugal energy to propulsion fluid in the casing thereby increasing the rate-of discharge of said fluid from said casing,

6. In a radial motor a casing, a pintle mounted centrally in the casing, and a rotor assembly rotatable within the casing around said pintle including, a cylinder block, a track ring eccentric with respect to the axis of said pintle, and support means for said track ring having outwardly opening radial slots each adapted to discharge fluid under centrifugal force into fluid in the space between the track ring and the peripheral wall of the casing, thus serving to propel the fluid in said space and to give it centrifugal energy, said pintle being adapted to deliver high pressure propulsion fluid to said cylinder block, and to deliver low pressure fluid from said cylinder block into the space within the casing surrounding the cylinder block, said pintle also having a port to receive low pressure fluid discharged from the casing, and a conduit extending through the casing wall and communicating between the interior of the casing and said pintle port.

'1. In a radial motor a casing, a pintle mounted centrally in the casing, a radial cylinder block rotatable around said pintle, said pintle being adapted to deliver high pressure propulsion fluid to said cylinder block, and to deliver low pressure fluid from said cylinder block into the space within the casing surrounding the cylinder block, said pintle also having a port to receive low pressure fluid discharge from the casing, and a conduit extending through the casing wall and com municating between the interior of the casing and said pintle port.

8. In a radial motor a casing, a pintle mounted centrally in the casing, and a rotor assembly rotatable within the casing around said pintle including, a cylinder block, a track ring eccentric with respect to the axis of said pintle, and means having radial slots opening radially outward and each adapted to discharge fluid under cen riiugal force into fluid in the space between the track ring and theperipheral wall of the casing, thus serving to propel the fluid in said space and to give it centrifugal energy.

, 9. In a radial motor, a casing, a pintle mounted centrally in the casing, and a radial cylinder block rotatable in said casing around said pintle,

said pintle having a plurality of bores communicating with the interior of the casing, and a plurality of circumferentially spaced ports communicating between said bores respectively and the interior of said cylinder block, and pressure responsive valve means in said bores adapted to connect the cylinder block with whichever bore is supplied with high pressure propulsion fluid, and

to connect the cylinder block with the space in H the casing around said cylinder block through the other of said bores.

10. In a radial motor, a casing, a pintle mounted centrally in the casing and having a discharge port to receive low pressure propulsion fluid, a dis charge conduit extending through the casing wall and communicating between the interior of the casing and said discharge port of said pintle, and a radial cylinder block rotatable in said casin around said pintle, said pintle having a plurality of bores communicating with the interior of the casing and a plurality of circumferentlally spaced ports communicating between said bores respectively and the interior of said cylinder block, and pressure responsive valve means in said bores adapted to connect the cylinder block with whichever bore is supplied with high pressure propulsion fluid, and to connect the cylinder block with the space in the casing around said cylinder block through the other of said bores, sliding sleeves in said bores respectively each having a plurality of longitudinally spaced ports, one of the ports of each sleeve being adapted to communicate with one of said circumferentially spaced pintle ports while the other of the said ports of the other sleeve is communicating with said discharge port of said pintle.

ii. In a radial motor, a pintle comprising a plurality of bores extending longitudinally from end to end. a pair of circumferentially spaced ports communicating between the surface of the pintle and said bores respectively, a third port positioned nearer the anti-drive end of the pintle than said circumierentially spaced ports and communicating between the surface of the pintle and both of the said bores, sliding sleeves in said bores respectively each having "a plurality of longitudinally spaced ports, and means for urging said sleeves respectively into a position in which one sleeve port is in register with said third port of the pintle, said sleeves being closed at the drive end but open at the anti-drive end whereby when high pressure fluid is introduced into one of said sleeves it is moved against the urging of said means into a position in which it is in communication with one of the said circumferentially spaced ports of said pintle.

12. A radial motor comprising a rotatable cylinder block, high pressure and low pressure fluid conduits communicating with said cylinder block, and means for controlling the flow of propulsion fluid through said conduits adapted to prevent cavitation when the supply of fluid is cut 01? whereby said motor may be driven mechanically if desired said means comprising valve means, and spring means adapted to open said valve means as soon as the fluid supply to the motor inlet passages is closed.

13. In a radial motor, a pintle comprising a plurality of bores extending longitudinally from end to end, a pair or circumierentially spaced ports tively eachhaving a plurality of longitudinally spaced ports, and means for urging said sleeves respectively into a position in which one sleeve port is in register with'said third-port of the pintle, said sleeves being closed at the drive end but open at the anti-drive end whereby when high pressure fluid is introduced into one of said sleeves it is moved against the urging of said means into a position in which it is in communication with one of the said circumferentially spaced ports of said pintle, said sleeves each having inwardly opening valve means for its port which is adjacent its anti-drive end and adapted to communicate with the said third port of said pintle.

14. An hydraulic motor comprising a casing providing a circular closure, a pintle mounted centrally in the casing, a radial cylinder'block, mounted for rotation around said pintle and concentric therewith, a track ring and support means therefor mounted in saidcasing for rotation about an axis eccentric to the axis of said pintle, and pistons in the cylinders of said block adapted to contact said track ring and to cause it to rotate whensaid cylinder block is rotating, the space within said casing between said track ring and the casing wall comprising in effect two complementary chambers each having its greatest cross sectional area diametrically opposite said pintle axis from said eccentric axis, and a discharge port for low pressure propulsion fluid located in the casing wall at a point diametrically opposite the pintle axis from said eccentric axis and therefore in a position to receive fluid from said chambers respectively in the locality of their greatest cross sectional area. 15. An hydraulic motor comprising a casing providing a circular closure, a pintle mounted centrally in the casing, a radial cylinder block, mounted for rotation around said pintle and concentric therewith, a track ring and support means therefor mounted in said casin for rotation about an axis eccentric to the axis of said pintle, and pistons in the cylinders of said block adapted to contact said tract ring and to cause it to rotate when said cylinder block is rotating, the space within said cas between said track ring and the casing wall comprising in effect two complementary chambers each having its greatest cross sectional area diametrically opposite said pintle axis from said eccentric axis, and a discharge port for low pressure propulsion fluid located in the casing wall at a point diametrically opposite the pintle axis from said eccentric axis and therefore in a position to receive fluid from said chambers respectively in the locality of their greatest cross sectional area, the said support means for said track ring including radially extending members having radially disposed slots opening outwardly into the said space between the track ring and the casing wall, and adapted, when the cylinder block is rotating, to discharge propulsion fluid into the mass of said fluid present in said space and rotating with the cylinder block, to thereby add to the centrifugal force of the fluid in said space, thereby increasing the pressure differential between the high and low pressure sides of the motor. 16. In an hydraulic motor a pintle comprising two fluid passages, each of said passages having 12 valve means adapted to automatically control the direction of fluid flow therein, depending upon which passage is supplied with high pressure fluid. whereby said passages respectively may operate alternatively, as inlet and discharge passages.

17. An hydraulic power converter comprising. a casing, a pintle mounted centrally in the casing. and an assembly rotatable about said pintle and comprising a cylinder block concentric with the axis of said pintle and a track ring positioned within said casing eccentrically with respect to the axis of the pintle, said cylinder block having a number of radial cylinders and pistons in said cylinders respectively adapted to bear on said track ring. the heads of said pistons having the configuration of a spherical segment, and said I track ring having a groove adapted to receive said pistons and to contact the spherical portion of said piston heads, said pistons and said track ring being so related that contact of the pistons with the track ring is limited to said spherical portions of said piston heads.

18. An hydraulic power converter comprising, a casing, a pintle mounted centrally in the casing, and an assembly rotatable about said pintle and comprising a cylinder block concentric with the axis of said pintle and a track ring positioned within said casing eccentrically with respect to the axis of the pintle, said cylinder block'havin a number of radial cylinders and pistons in said cylinders respectively adapted to bear on said track ring, the heads of said pistons having the configuration of a spherical segment and said track ring having a raceway adapted to receive 3 said spherically segmented heads respectively and to contact said pistons only on the spherical surfaces of said heads said pistons being freely rotatable in their cylinders respectively and thus each being adapted to make a rolling contact with 40 the track ring when the frictional contact between the spherical surface of its piston head and said track ring is unballanced on diametrically opposite sides of the longitudinal axis of ,said piston due to inherent surface irregularities and thereby produce rotation in an oscillatory manner about said longitudinal axis.

19. In a radial power converter a casing, a pintle mounted centrally in the casing, and an assembly rotatable about said pintle and comprising, a cylinder block having a number of radial cylinders, pistons in said cylinders respectively, and a rotatable track ring having a circumferential groove in its inner face engaged .by said pistons, the heads of said pistons being shaped to conform generally with said groove and having the configuration of a spherical segment the radius of the spherical surface of said piston heads respectively and the radius of said groove being substantially the same.

20. An hydraulic motor comprising a casing, a pintle mounted in the casing, a. radial cylinder block mounted for rotation around said pintle, a track ring and disk-like support means therefor mounted in said casing for rotation about an axis '65 eccentric to the axis of said pintle, said disk-like support means being provided with radially extendin slots open at their outer ends respectively. and pistons in the cylinders of said block adapted to contact said track ring and to cause it andits said disk-like support means to rotate when said cylinder block is rotating, a discharge port located in the casing wall at a point diametric ally opposite the pintle axis from said track ring axis, the space within said casing between said track ring and the interior of the casing wall 13 comprising in effect two chambers at least one of which increases in cross section from a point 180 from said outlet to said outlet.

21. An hydraulic motor comprising a casing, a pintle mounted in the casing, a radial cylinder block mounted for rotation around said pintle, a track ring and disk-like support meanstherefor mounted in said casing for rotation about an axis eccentric to the axis of said pintle, said disk-like support means being provided with radially ex-' tendingslots open at their outer ends respectively, and pistons in the cylinders of ,said block adapted to contact said track ring and to cause it and its.

said disk-like support means to rotate when said cylinder block is rotating, and a discharge port pistons therin, a track ring against which said pistons travel, and mean for mounting said track ring in said casing eccentrically with respect to said pintle, a fluid inlet passage leading to the said cylinders, a fluid passage leading from said cylinders to the interior of the casing, an outlet port in the periphery of said casing, and an outlet passage leading from said outlet port, and pump means for increasing the differential in pressure between said cylinders and the outlet of said casing.

23. An hydraulic motor comprising a casing, a pintle extending into said casing at its center, a rotor mounted for rotation on said pintle, said rotor having a number of radial cylinders with pistons therein, a track ring against which said pistons travel, and means for mounting said track ring in said casing eccentrically with respect to said pintle, a fluid inlet passage leading to the said cylinders, a fluid passage leading from said cylinders to the interior of the casing, an outlet port in the periphery or said casing, an outlet passage leading from said outlet'port, and pump 4 means to facilitate the expulsion 1' expended 5 01 the casing.

14 fluid from said outlet port of the motor, said means comprising radially extending slots in said track ring mounting means, said slots being open to discharge fluid in the direction of the periphery 24. In a. radial hydraulic motor'in which the space between the rotor and the casing is filled with propulsion fluid and in which the pistons of the rotor are adapted to contact a tract rin 0 maintained in eccentric relation 'to the rotor by tially perpendicularly with respect to the track ring, means for supplying propulsion fluid to the cylinders of the motor and for leading the exl5 pended fluid from said cylinders into the casing, located in the casing wall and bisected by a line an exhaust port for the motor located in the periphery of the casing, and means to facilitate the expulsion of expended fluid from said exhaust port comprising radial slots in said tract ring 20 retaining rings, said slots being closed at their innerends but extending outwardly to the p6 riphery of said retaining rings respectively in the direction of the periphery of said casing.

ROGER F. HORTON.

REFERENCES CITED The following references are of record in the flle of this patent:

UNITED STATES PATENTS Number Name Date 663,716 Asling et a1 Dec. 11, 1900 2,105,454 Ferris Jan. 11, 1938 2,160,612 Alpem May 30, 1939 v 2,186,556 Robbins Jan. 6, 1940 2,208,568 Benedek July 23, 1940 2,232,428 Benedek Feb. 18, 1941 2,254,103 Douglas Aug. 26, 1941 2,255,963 Benedek Sept. 16, 1941 2,262,593 Thomas et al. Nov. 11. 1941 2,303,685 Eden et a1 Dec. 1, 1942 2,359,513 Eden et a1 Oct. 3, 1944 FOREIGN PATENTS 5 Number Country Date 161,490 Great Britain April 5, 1921 

